Printing telegraph apparatus



Sept. 29, 1942. A. H. REIBER PRINTING TELEGRAPH APPARATUS Original FiledMay 4, 1936 10 Sheets-Sheet 1 FIG. l

INVENTOR ALBERT H. REIBER P 29, 1942- A. H. REIBER 2,296,874

PRINTING TELEGRAPH APPARATUS Original Filed May 4, 1936 10 Sheets-Sheet2 I INVENTOR ALBERT H. REIBER ATTORN EY Sept. 29, 1942. A. H. REIBERPRINTING TELEGRAPH APPARATUS Original Filed May 4, 1956 10 Sheets-Sheet3 OTOR CONTROL MECHANISM H 23 E To M INVENTOR ALBERT H. REIBER ATTORN EYSept. 29, 1942- A. H. REIBER 2,296,874

PRINT ING TELEGRAPH APPARATUS Original Filed May 4, 1936 10 Sheets-Sheet4 I FIG. 22

INVENTO'R ALBERT H. RElBER ly/fa P 29, 1942- A. H. REIBER 2,296,874

PRINTING TELEGRAPH APPARATUS l0 Sheets-Sheet 5 Original Filed May 4,1936 H6 5 INVENTOR ALBERT H REIBER A-i'ToRN Y p 9 19 2- A. H. REIBER2,296,874

PRINTING TELEGRAPH APPARATUS Original Filed May 4, 1936 10 Sheets-Sheet6 INVENTOR ALBERT H REIBER ATTORN P 29, 1942- A. H. REIBER 2,296,874

PRINTING TELEGRAPH APPARATUS 10 Sheets-Sheet '7 Original Filed May 4,1936 INVENTOR ALBERT H. REIBER ATTORNE Sept. 29, 1942. A. H. REIBERPRINTING TELEGRAPH APPARATUS Original Filed May 4, 1936 10 Sheets-Sheet8 INVENTOR 388 BY ALBERT H REIBER 389 w 'ATTORNE Sept. 29, 1942. A. H.REIBER PRINTING TELEGRAPH APPARATUS 1o sheets-sheet 9 Original Filed May4, 1936 FlG. l6

INVENTOR AtBERT H- REIBER 17% ATI'OR Y FIG. |5

Sept. 29, 1942.

A. H. REIBER 2,296,874

PRINTING TELEGRAPH APPARATUS Original Filed May 4, 1936 10 Sheets-Sheet10 INVENTOR Y 'ALBERTH. REIBER ATI'OR Y Patented Sept. 29, 1942 rnm'rnveTELEGRAPH APPARATUS Albert 11. Reiber, Evanston, 1u., assignmto TeletypeCorporation, Chicago, 111., a corporation of Delaware Application May4,1936, Serial No'. 77,796

Renewed May 8, 1940 11 Claims. (Cl. 178-29) This invention relates toprinting telegraph apparatus and particularly to a type wheel printer.for recording printed characters in page form.

The principal object of the invention is to endow a type wheel printerwith many of the advantageous features of a type bar printer whileretaining the simplicity of construction characteristic of type wheelprinters.

A further object is to provide a type wheel printer having the principaloperating! characteristics of certain commercially used type barprinters so as to be capable of being'operated over the same telegraphcircuits and in interconnection with the commercially used type barprinters to record the same message in line for line arrangement andperform the same functions as the type bar printer.

The invention features power actuated means for simultaneouslytransferring to all of the code discs of a code disc selector,settingsin accordance with sequentially received telegraphic impulses.

The invention also features a type wheel having blank elements presentedto the printing platen for each function selection whereby the normaloperation of the print bail need not be suppressed.

The invention also features function mechanism in which the performanceof any function may be blocked by an element or elements associated withthe case shift mechanism of the printer. Thus, two functions, or acharacter selection and a function may be associated with one codecombination. Under these circumstances, selection between the twofunctions, or between the character and the function, is determined byselective case shift conditioning preceding the function selection.

Briefly, the principal elements of the receiving apparatus are aselecting mechanism including a single magnet selector and a code discselector, power driven operating cams controlled from the selectingmechanism, a type wheel and means for stopping it in accordance with theoperation of the code disc selector, cam operated means for efiectingprinting from the type wheel, cam controlled and operated mechanisms forperforming the necessary stunts or functions of the printer, mechanismfor feeding an inked ribbon between the type wheel and a printing platenincluding means for controlling the direction of feeding of the ribbon,and a movable carriage which carries the paper upon which printing is tobe effected.

'The single magnet selector operates in accordance with signal impulsesreceived sequentially to position settable elements correspondingly.Power operated transfer mechanism then operates through the elementsthus set to transfer simultaneously all of the conditions established bythe received signal impulses to a code disc selector which has aplurality of stop elements, any one of which, upon selection, isprojected into the path of an arm on a type wheel shaft, towhich aconstant torque is applied, to stop the type wheel in a positioncorresponding to the received signal combination. The single magnetselector mechanism controls the operation of a set of operating .cams,one of which operates the transfer mechanism to effect the setting ofthe code discs, another of which operates. a printing bail and inaddition, under certain selectlve conditions, performs certainnon-printing functions and conditions other non-printing functions forperformance, and the third and final cam of which operates the spacingmechanism and performs those functions that are conditioned but notperformed by the printing bail. Spacing from one character to anotherand between words is accomplished through a pawl and ratchet, the latterof which is connected to a pinion meshing with a rack included in theplaten carriage. The spacing operation tends to be performed withinvariable regularity but is, under certain circumstances, suppressed,as for example, during. the performance of functions which, ifaccompanied by spacing, might result in the introduction of undesirablespaces in the printing of letter combinations. Those functions which areperformed by operation bfQthe spacing cam are the functions which it isdesirable to perform slowly, in order to obviate attempted violentmovement of relatively massive elements. Those functions that areperformed by the print bail operating cam are functions involving themovement of relatively light elements, the inertia of which iscomparatively low so that they may be operated with relatively greatrapidity, as the printing bail operating cam is arranged to perform anoperation in a very .brief interval. In the case of certain functions, ayielding connection is provided between a function conditioning leverand an associated lever, and the latter lever may be blocked by anydesired means and in particular by the case shift mechanism of theprinter, so that the function conditioning opera tion may be dissipatedin the yieldable connection and the performance of a function may bemade dependent not only upon a particular code combination associatedwith that function, but also upon the predetermined condition of thecase shift mechanism as determined by a previously receiveddiiferentcode combination.

The particular type wheel mechanism disclosed herein is fully describedand claimed in a copending application of Howard L. Krum et al., SerialNo. 77,794, filed on even date herewith.

For a more complete understanding of the invention, reference may be hadto the following detailed description, taken in conjunction with theaccompanying drawings'in which Fig. 1 is a perspective view of thecombined transmitting and receiving apparatus in accordance with theinvention;

Fig. 2 is a front elevatlonal view of the receiving and printingmechanism;

Fig. 3 is a, side elevation of the transmitting and receiving mechanism;

Fig. 4 is a vertical sectional view through the receiving and printingmechanism;

Fig. 5 is a top plan view of the transmitting and receiving mechanism;

Fig. 6 is a detailed plan view of the selecting mechanism and portions.of the carriage mechanism;

Figs. 7 and 8 are respectively, elevational and plan views of the caseshift mechanism;

Fig. 9 is a horizontal sectional view showing the spacing and functionperforming mechanisms;

Fig. 10 is a horizontal sectional view showing details of the spacingmechanism;

Fig. 11 is a horizontal sectional view showing details of the transfermechanism;

Fig. 12 is an exploded view in perspective of the function selecting andperforming -mechanisms;

Fig. 13 is a perspective view of the ribbon feed mechanism;

Figs. 14 and 15 are plan views of the ribbon feed mechanism showingdifferent conditions of operation;

Fig. 16 is a vertical sectional view through the ribbon feed mechanism;

Fig. 1'7 is a perspective view of the platen carriage showingparticularly paper holding and guiding meams;

Fig. 18 is a perspective view of a removable paper roll holder shown inbroken lines in Fig.

Fig. 19 is a perspective view of a paper guiding plate;

Fig. 20 is a vertical sectional view through the platen carriage showingthe manner of mounting the plate shown in Fig. 19 upon the carriage;

Fig. 21 is a vertical sectional view showing the line feeding mechanism;

Fig. 22 is an elevational view of a modified print hammer operatingmechanism; and

Fig. 23 is a schematic wiring diagram.

Keyboard transmitter Referring now to the drawings and particularly toFigs. 1 and 5, the reference numeral l5 indicates generally a keyboardtransmitter mechanism which may be of any desired form such as the onedisclosed in U. S. Patent 1,595,472, granted August 10, 1926, to HowardL. Krum. The keyboard transmitter I5 includes a base casting l6 whichcarries a plurality of character selecting keylevers l8. The keyleversoperate upon a set of permutation bars (not shown) to controltransmitting apparatus indicated generally by the reference numeral IS.The transcarries a plurality of transmitting cam 22. A contactcontrolling bell crank lever 23 is associated with each of thetransmitting cams 22. Gne end of each of the bell crank levers'23 isdisposed in engagement with one spring of a pair of transmitting contactsprings 2! (Fig. 1) and theother end is aligned with a lever 26 which iscontrolled by the permutation bars (not shown). In their idle positions,the transmitting cams 22 maintain the bell crank levers 23 in a positionsuch that all but one of the pairs of transmitting contacts are open,the excepted contact pair being closed for the application of a stoppulse to the line. Upon the operation of a keylever IS, the permutationbars and therefore the levers 26 which they control are setpermutatively, whereby certain of the bell crank levers 23 are blockedso that they cannot rotate and others are freed so that they may rotateto allow closing of the associated transmitting contacts 24 whenpermitted to do so by their associated transmittting cams 22. Thetransmitting cams are so arranged upon the shaft 2| that they releasethe several transmitting contact bell crank levers 23 successively forrotation and thus the transmitting contacts corresponding to theparticular permutation code established by the operated keylever areclosed successively. A locking bail 28 has a cam follower 29 which rideson a cam 3| carried by cam shaft 2|. Ball 28 drops into blockingrelation to the levers 26 after they are set by the permutation bars andprevents disturbance of an established code combination during thetransmission of the corresponding code impulses. Power for driving thetransmitting cam shaft 2| is communicated through a spring loaded clutch32 from a gear 33 which is driven through suitable intermediate gearing35 from a gear 4| (Figs. 1 and 2).

The base casting l6 removably supports the foundation for a receivingprinter comprising a vertically extending frame casting 36 and a framecasting 31 secured to the casting 36. The frame casting 36 extends fromfront to rear of the base casting l6 and the casting 31 extendstransversely thereof. The frame casting 36 has secured thereto bearingblocks 38 which rotatably support a shaft 39. Shaft 39 has securedthereto a gear 4| (Figs. 1 and 2) which is driven by a spiral gear 42(Fig. 4) which is mounted on the rotor shaft of motor 34 and constitutesthe main driving gear of the receiving printer as well as of thetransmitting mechanism. The shaft 39 actuates the selector mechanism ofthe receiving printer and also the operation performing cams.

The driving gear 42 (Fig. 4) also meshes with a gear 43 which is mountedon a shaft 44 and mitting apparatus includes a cam shaft 2| which isoperatively connected thereto through a friction clutch l6. Shaft 44 isjournalled in a code disc selector mechanism indicated generally by thereference numeral 41 (Fig. 3) which is removably supported on the framemember 36.

Selecting mechanism At the top of frame member 36 there is mounted asingle magnet selector mechanism which is generally similar to theselector disclosed in U. S. Patent 1,937,376, granted November 28, 1933,to Walter J. Zenner. The selector mechanism (Fig. 6) comprises a set ofselector elements in the form of thin, flat fingers 5| arranged insuperposed relation between guide plates 52. The selector fingers 5|equal in number the signalling elements in the code on which thereceiving printer operates. Thus, if a five-unit code is employed, therewill be five of the selector fingers whereas a six-unit code willrequire six selector fingers. The guide plates 52 are mounted on studs53 secured to the selector mounting plate 54 and are spaced by washers(not shown). The circular left ends 56 of selector fingers 5| engagecorresponding sockets of thin, fiat bell crank levers 51 pivoted on acommon shaft 58. Individual springs 59 bias the bell cranks 51 in theirclockwise direction whereby the selector fingers 5| are urgedrightwardly. The pointed ends 6| of the bell crank levers 51 are thusmaintained in contact with a cam barrel 62 which is mounted on shaft 39and is driven thereby through friction discs, indicated at 63 (Fig. 4)

Cam barrel 62 is provided with a helically arranged series of camprojections 64 (Fig. 6), one for each of the bell cranks 51, whichrotate the bell cranks 51 in succession and thus draw the selectorfingers 5| leftwardly successively as the cam barrel 62 is rotated. Inaddition to the longitudinal movement, the selector fingers have alaterally swinging movement between a pair of studs 66.

The setting of any selector finger 5| either to its clockwise orcounterclockwise position is determined by the electromagnet 61 which ismounted on the mounting plate 54 and which is provided with armature 68fixed to a flutter lever 69 which is pivoted at 1| to a frame carried bythe supporting plate 54. Mounted on a pivot 12 adjacent to and incooperative relation with the flutter lever 69 is a selector 13. Lever13 terminates in a T-shaped portion 14 having down- I pivoted at 85,which have disc portions 82 engaging sockets in levers 18.

As previously stated, each selector finger 5| is shifted clockwise orcounterclockwise by having one or the other of its arms 11 drawn againstone or the other of the abutments 16 of the T-shaped portion 14 ofselector lever 13. The selector lever 13 is connected by a spring 83 toan arm 84 of the flutter lever 69 and the minimum distance between thelevers 69 and 13 is determined by an abutment screw 86. The flutterlever 69 has a portion which follows a flutter cam 81 (Figs. 2 and 4)included in the cam barrel assembly 62.

As the signal impulses are received over the telegraph line, theelectromagnet 61 is energized and deenergized depending upon the natureof such impulses. During the reception of a set of impulses constitutinga signal, the cam barrel 62 is rotated, flutter lever 69 follows fluttercam 81, and armature 68 is moved cyclically into engagement with itspole face. If the armature 68 is then held due to the presence of anenergizin impulse through the winding of its electromagnet connected inthe line, the flutter lever 69 will be prevented from following thecontour of the flutter cam 81. The abutment screw 86 and spring 83 causethe selector lever 13 to follow the motions of the flutter lever 69 sothat when the levers are moved counterclockwise, one of the abutments 16of selector lever 13 is moved into alignment with one set of arms 11 ofthe selector flutter cam 61.

fingers 5| and whenv the levers are rotated to their extreme clockwisepositions,. the other abutment 16 is moved into alignment with the otherset of arms 11. The several cams 64 on the cam barrel 62 are sopositioned with respect to the flutter cam 81 that the selector fingers5| are drawn leftwardly in synchronism with the signalling impulsesreceived by the selector magnet 61 so that a selector finger 5| will bemoved from a position correspondin to a spacing signal to a positioncorresponding to a marking signal only if the armature 68, after beingrotated into engagement with its pole face by flutter cam 81, is held bythe electromagnet as the selector finger 5| is drawn leftwardly by itsassociated bell crank lever 51 and will not be so shifted as a result ofmere movement of the armature 68 as the flutter lever 69 follows a highportion of A cam operated lock lever 88 looks and releases selectorlever 13 at proper intervals under control of a cam 89 on the cam barrel62.

The transfer bell crank levers 8| are connected by socket connections tothe code discs of a code disc selector mechanism which, asvpreviouslymentioned, is designated generally by the reference numeral 41. Theselector mechanism 41 includes code discs 9| equal in number to thenumber of selector fingers 5|, and each of the discs is supported so asto be rotatably responsive to the transfer bell crank lever 8| to whichit is articulated. The discs 9| have their edges notched permutativelyso that for each permutative setting of the discs a single completealignment of notches of the several discs will be effected.

The code disc selector mechanism 41 has plates 92 and 93 (Fig. 4)disposed respectively above and below the code discs 9| and a plate 94disposed below and at some distance from the plate 93. The three plates92, 93, and 94 have radially arranged slots equi-distantly spaced, theslots corresponding in number and positions to the permutative alignmentof the notches in the code discs 9|. A selectable stop pin 96 isdisposed in each vertical alignment of slots in the discs 92, 93, and 94and each pin has a portion extending below the disc 94, which portion iseyelet-shaped, and a straight portion extending above the disc 92. Agarter spring 91 surrounds all of the stop pins 96 and retains themproperly seated in the disc 94.

Each of the pins 96 carries anti-friction rolls 95 (Figs. 4 and 6) equalin number to and in alignment with the code discs 9|. With anypermutative disposition of the code discs 9| an alignment of notcheswill be presented opposite the anti-friction rolls carried by one of thestop pins 96. The stop pin opposite which the notches are aligned pivotsabout the inner limit of the slot in the plate 94 so that its upper endmoves toward the type wheel shaft 44 in a direction radially of saidshaft as the anti-friction rolls 95 become seated in the alignment ofnotches in the code discs. Only one of the stop pins 96 can be selectedat a particular time due to the fact that there cannot be two alignmentsof code disc notches simultaneously.

The type wheel shaft 44 carries in fixed relation thereto a stop arm 98,the outer end of which clears unselected stop pins 96 but is blocked bya selected stop pin and is prevented from further rotation until theselected pin has been cammed outwardly by one or more of the code discsdue to a change in their permutative arrangement. A leaf spring 90 (Fig.6) carried by the stop arm 90 precedes the stop arm 08 as the shaft 44rotates and the end of the leaf spring 99 passes over the top of anystop pin. that is selected and drops ahead of the pin when the arm 98 isstopped, thereby confining the pin between the arm 90 and the leafspring 09 and preventing the stop arm from bouncing away from the stoppin 90 by which it has been arrested. The shaft 44 carries a type wheelwhich is designated generally by the reference numeral IN. The selectiveoperation of the stop pins 90 determines stop positions of the typewheel.

Transfer mechanism The shifting of the code discs 0| to establishsuccessive selections of the stop pins 00 is effected through the mediumof a power actuated transfer bail I02 (Figs. 1, 2, 3, 6, and 11). Thebail I02 is pivoted on a shaft I03 and has a lever I04 adiustablyconnected thereto by screw I05. The lever I04 carries a cam followerroller I00 which rides against a cam I01. The

bail I02 has at its upper end a vertically extending arm I00 to which issecured by bolts I09 a U-shaped extension III (Fig. 6). The arm I08 andthe opposite side portion of the extension III are provided withrectangular apertures which receive U-shaped springs II2. One arm ofeach of the springs II2 extends through the aperture in the arm I00 oftransfer bail I02 and terminates in alignment with one of the bell cranklevers 51. The other arm of each of the springs H2 terminates in theaperture in the arm I08 and is confined there by that arm of theU-shaped extension III which is secured by the screw I09 and whichpartially covers the aperture in arm I08. The springs II2 are undertension in the aperture in the vertical arm I00.

The springs H2 serve as individual yielding operating connectionsbetween the transfer bail I02 and the several bell crank levers 51. Whenthe transfer bail I02 is rocked in a clockwise direction by cam I01, theends of the springs II2 engage the bell crank levers 51 and rock themclockwise and the bell crank levers in turn shift the selector fingers Irightwardly. The selector fingers 5| rock the levers 18 clockwise orcounterclockwise, depending upon the positions into which th fingers 5Ihave been moved through the action of the selector magnet 01, selectorlever 13, and bell crank 51. As previously described, shifting of thelevers 10 causes corresponding shifting of the transfer bell cranklevers 8| which are articulated to the code discs 9| so that permutativearrangements of the code discs in accordance with signals received bythe selector magnet 01 are set up when the transfer bail I02 is actuatedin a clockwise direction. Springs 59 bias the bell crank levers 51 inclockwise direction, as previously described, and while the springs maybe of suflicient tension to shift selector fingers 5|, the levers 18,transfer levers 8|, and code discs 9|, it has been found desirable notto rely on the springs to effect the transfer of selections to the codediscs, and to this end a locking bar has been provided to prevent thesprings from effecting such transfer at all times except when thetransfer bail is to be operated.

pied by the knife-edge II4 when the transfer bail I02 is in its extremecounterclockwise position. The knife-edge II4 thus serves when inlooking position to restrain the levers 10 from being moved by thesprings 53. Since the extension arm I." is carried by the transfer bailI02, it is withdrawn to a position which clears the ends III of thelevers 10 when the transfer bail is rocked in a clockwise direction andat this time the code discs are shifted by the combined action of thetransfer bail I02 operating through springs H2 and the springs 03. ArmH3 returns to locking position when the transfer ball I 02 is restoredto its normal or unoperated position.

Type wheel The type wheel shaft 44 has a reduced portion I2I at theupper end thereof which provides a shoulder I22 (Fig. 4) A hub I23 isJournalled on the reduced portion I2I of shaft 44 and is slidablethereon. At its upper end the hub I23 carries a disc I24 to which issecured an annular type wheel frame I20. The frame I20 has slots inradial arrangement equally spaced therearound, and in each of the slotsupper and lower type pallets I21 are slidably disposed. The type palletsI21 are arranged in upper and lower annular rows, one row of which maycarry any desired group of characters such as letters and the other ofwhich may carry other characters such as figures and punctuation marks.The type pallets comprise type faces I20 to which are secured thinshanks I23 which extend inwardly and radially of the type,. wheelstructure within the radial slots thereof.. The shanks of each annularrow of type pallets are notched to receive a garter spring I3I whichbiases all of the type pallets of an annular row to their innermostpositions with the type faces I20 disposed about the periphery of theslotted frame I20. An annular ring I32 is floatingly disposed in thenotches in both annular rows of type pallets and prevents the type Plets from accidental displacement from the type wheel structure due tocentrifugal force in the event that one of the garter springs I3I shouldbreak. At one portion of its periphery, the type wheel structure has notype pallets and at that point the disc I24 and frame I20 are providedwith recesses in which is disposed a perpendicular portion I33 of a typewheel driving arm I34 which is adjustably secured by screws I30 to anarm I35 which is carried by the type wheel shaft 44 at the top thereofin fixed relation to the shaft to be driven thereby. The adjustabilitybetween the arms I34 and I35 is angular.

The type wheel structure is slidable longitudinally of the type wheelshaft to bring either of the two rows of type pallets into printingalignment with the printing platen, the shifting of the structure beingaccomplished by a sliding movement of the hub I23 with respect to thetype wheel shaft 44 produced by mechanism to be described hereinafter.As the type wheel is shifted, the recesses in which the perpendicularportion I33 of driving arm I34 is disposed slide upon the portion I33and driving relation between the type wheel shaft and the type wheel ismaintained. A printing hammer I30 is pivotally mounted on screws I31threaded into the stationary bracket I25 (Fig. 3) and has its head inalignment with the printing position so that it is disposed behind theshank of the type pallet of either of the annular rows of type pallets,depending upon whether the type wheel is in its upper or lower position.The printing hammer I36 has integral therewith a bail portion H9 at theopposite end of which is integrally formed a lever arm II1 (Figs. 1 and3) which carries an impact receiving member I38. A limit screw II8limits the operative movement of lever arm I I1. The lever arm H1 isactuated by a striker memher to be described later. The operative move-Carriage mechanism The printing platen I39 is rotatably mounted in endplates I40 of a reciprocating carriage I (Fig. 1). The carriage I issupported in adjustable rails I42 at the top of the main frame member31. Anti-friction balls I43 (Fig. 4) are disposed between the carriageHI and the rails I42 and provide free movement of the carriage withrespect to its supporting rails. The rotatable platen is provided with afeed ratchet I46 (Fig. '2) with which there cooperates a feed pawl I41(Fig. 21).

The platen feeding pawl is articulated to a lever I49 (Fig. 21) that isfixed to a rock shaft I50. The rock shaft I50 is rotatably journalled inthe carriage I4I andhas fixed thereto at a point substantially midwaybetween theends of the carriage I an operating lever I60. The lever I49,rock shaft I50, and operating lever I60 are biased counterclockwise by aspring I65. Feeding of the ratchet I46 in the direction indicated by thearrow is eifected by clockwise rotation of operating lever I60, by apower actuated bail to be described later, against the tension of springI65, which subsequently acts to reciprocate the pawl I41 to pick up thenext tooth or teeth for the next linefeeding operation. A lever I10,pivoted on the carriage end plate I40, provides two abutments fordeflecting the pawl at different points in its travel to idle orunoperated position to establish single or double line spacing. When thelever is in the position shown in dotted line, it permits the pawl totravel sufllciently far in engagement, with the ratchet I46 to pick uptwo teeth, whereas if the lever is in the full line position the 'pawlis deflected from the ratchet and is permitted, when it operates, topick up only one tooth. An adjustable eccentric I15 is mounted on thecarriage end plate I40 and is disposed in the path of a camming lug I85on the pawl I41 for wedging the pawl against the ratchet to preventover-travel of the ratchet and platen. A spring biased jockey roll I90bears against the ratchet I46 and controls the positioning of the platenI39.

The carriage MI is moved to its right-hand position by a belt II (Fig.2), which has one end connected to a drum I52 which contains a spiralspring by which the drum is urged to rotate in a clockwise direction andwhich has its other and connected to a pin I53 (Figs. 3 and 6) carriedby the carriage MI. The carriage I is moved leftwardly by spacingmechanism to be described hereinafter against the action of the spiralspring. A lever I56 pivoted at I51 (Fig. 3) has one end articulated tothe plunger rod I58 of a dashpot I59 and has its other end positioned tobe engaged by the carriage I as it travels into its extreme right-handposition by the action of -the spiral spring. With this arrangement, thereturn of the carriage to its extreme right-hand position is cushionedby the dashpot I58. Stop screws I54 threadedly engage the carriagesupporting portion I41 of the frame casting 31 at opposite ends of saidportion, and the inner ends of the stop screws are disposed in the pathof a bracket I45 mounted on the carriage I. The screws I54.limit themovement of the carriage in both directions of travel.

Ribbon mechanism At the top of the printer and adjacent to the typewheel assembly IOI there is provided a ribbon feed mechanism designatedgenerally by the reference numeral I6I (Figs. 1, 2, 3, 4, 5, 13, 14, 15,and 16) for supporting an inked ribbon similar to the ribbons employedin typewriting machines and for feeding the ribbon past the printingposition andbetween the type pallets and the printing platen. Thereference numeral I62 designates a plate which is the foundation of theentire ribbon feed mechanism and which is in turn supported on theprinter by means of posts I63 so that the complete ribbon feed mechanismis removable as a unit.

The plate I62 carries arcuate ribbon guide band I64 which guides theribbon around the type wheel assembly I M and which is provided with anaperture I66 through which the type pallets may strike against thepaper, upon which characters are to be recorded, with the ink ribboninterposed between the type pallets and the paper whereby a character isimprinted upon the paper. Ribbon spool supporting pins I61 are joumalledin the side arms of the plate I62 and each pin has secured thereto abovethe plate I62 9. disc I68 and .at the lower end of the pin below theplate I62 a ratchet wheel I69 which may b rotated by means of a pawl tocause the positive rotation of the pin I61 and disc I68. Each of thediscs I68 carries a pin I1I which engages a ribbon spool I12 to causethe spool to be driven when the ratchet I68 is positively rotated by itsoperating pawl.

The plate I62 carries a pivot pin I13 on which, below the plate I62,.are pivoted two levers, one of which is designated generally by thereference numeral I14, th other of which is designated generally by thenumeral I16. The lever I14 has oppositely extended symmetrical arms I11at the outer ends of which are portions I18 formed perpendicular to thearms I11 and bifurcated. The path of the ink ribbon, as it passes fromone spool to another, is through the bifurcations in the perpendicularportions I18 of the arms I11. The lever I14 also has an arm I19extending away from th arms I11 on the line of a bisector of the anglebetween th arm I11. This arm I19 is widened at its outer end as shown atIN and an additional arm I82 which is pointed at its outer endcooperates with a spring I to serve as a jockey to maintain the leverI14 in either of the two positions to which it may be shifted. Lever I16has the general contour of a bell crank lever, one arm I84 of which hasat its outer end shoulders I86 disposed in the plane of the ratchetwheels I69 to serve as a retaining pawl for either of the ratchet wheelsto prevent the wheel from slipping back as it is advanced by the feedpawl. The arm I84 of the bell crank lever I16 is provided intermediateits ends with an aperture I81 which is substantially the lever I16.

An operating lever I92 for the ribbon feed mechanism is pivoted to plateI62 at I93 and carries at its inner end a pivot pin I94 on which ispivotally mounted the ratchet feed pawl indicated generally by thereference numeral I96. The feed pawl I96. is U-shaped and both arms aremounted on the pivot pin I92. The "upper arm I91 has upwardly extendingabutment I98, the distance between which is somewhat greater than thedistance across the widened end I8I of the arm I19 of lever I14. Theupwardly turned abutment I98 extend at least as high as the outer end ofarm I19, so that they may engage the widened end thereof in a manner tobe described. The lower arm I99 of the feed pawl I96 is formed at itsouter end with ratchet wheel engaging portions 20I disposed in the planeof the ratchet wheels I69. Intermediate the ratchet engaging portionthere is a depending pin 202 which extends into the diamond-shapedaperture I81 in the lever I16. A floating link 203 has one end engagingthe upper end of pin 202 and the other end engaged by a tension spring204 which is connected to the plate I62. The spring 204 and link 203serve as an over-center device for the feed pawl I96 and bias theoperating arm I92, by which the stepping pawl is carried, to theunoperated position. A power actuated lever 206 carrying a link 205which engages the ribbon feed operating lever I92 cyclically operatesthe lever by rotating it clockwise in opposition to the tension ofspring 204. Lever 206 is pivotally mounted at 208 (Fig. 1) and isactuated by lever arm 249, which, as will appear subsequently, isoperated by a cam. Leaf springs 201 frictionally engage ratchet wheelsI69 and place sufiicient drag on the spool from which the ribbon isbeing drawn to insure tight winding of the ribbon on the other spool.

Referring particularly to Fig. 14 for a description of the operation ofthe ribbon feeding mechanism, it will be noted that pawl I96 has beenpulled into engagement with the left-hand ratchet wheel I69 by theover-center device comprising the link'203 and spring 204. In thisposition the right-hand upwardly extending abutment I98 is somewhatnearer to the rear of the mechanism than is the left-hand abutment. Itwill also be noted that the spring I89 is in front of the pivot pin I13and urges the arm I84 of retaining pawl lever I16 into engagement withthe left-hand ratchet wheel I69. The operating lever I92 is periodicallyrotated clockwise by the operating bail 206 and in being so rotated, itmoves the ratchet feed pawl I96 rearwardly of the typing unit, and thepawl, being in engagement with the left-hand ratchet wheel I69, rotatesit counterclockwise. Upon restoration of the lever I 92 to itsunoperated position, the pawl I96 is brought into engagement with thenext tooth of the ratchet wheel preparatory to the next ribbon feedingoperation. As the ratchet wheel is rotated coun- I84 adjacent to theleft-hand forward wall of the aperture without affecting the position ofthe pawl arm;

The direction of feeding of the ribbon may be reversed by rocking thelever I14 from the position shown in Fig. 14 which is the extremeclockwise position, to that shown in Fig. 15 which is the extremecounterclockwise position by either of two methods described below. Suchmovement of the lever I14 will carry the outer end terclockwise, theouter end of arm I84 of reof the arm I 19 thereof out of alignment withthe left-hand abutment I98 of pawl I96 and into alignment with theright-hand abutment. This operation does not in itself transfer thefeeding operation from the left-hand ratchet I69 to the right-handratchet. The transfer of the feeding operation will occur, however, uponth next operation of the operating lever I92 by bail 206. When the leverI92 is so operated, the pawl I96 will begin to move in ratchet feedingdirection in the same path that it had been following previously, butbefore it reaches the limit of its travel, the right-hand abutment I98will be blocked by the widened end I8I of the arm I19 of lever I14, andfurther movement of the feed pawl will cause it to be rotated about itpivot pin I94 in a clockwise direction and into en agement with theright-hand ratchet I 69 with the gisistance of the over-center link 203and spring multaneously to its counterclockwise position due to the factthat the pin 202 is disposed within the diamond-shaped aperture I81 andwill rock the lever I16 counterclockwise as the pawl I96 is shifted. Thecounterclockwise rotation of the well crank lever I16 causes itsover-center spring I89 to shift to the rear of the pivot pin I13.

The feeding of the ribbon in opposite directions may be controlled bymanual shifting of the lever I14 if desired, but the apparatus isintended for automatic reversal of the ribbon feed by cooperation of aportion of the ribbon itself with the perpendicular arms I18 -of thelever I14. Ink ribbons of the kind used in typewriters are provided neartheir opposite ends with small metal eyelets or other obstructions whichare much wider than the thickness of the ribbons. The bifurcations inthe arms I18 are too narrow to permit these eyelets orother'obstructions to pass. As a result, when the end of a ribbon isnearly reached and one of the obstructions engages an arm I18 of thelever I14, the latter is rotated due to movement of the ribbon, and assoon as the lever has been rocked by the moving ribbon a distancesufflcient to block one of the abutments I98 of the pawl I96, theratchet feeding will be transferred upon the next operation of theoperating lever in the manner described in the foregoing paragraph. Itwill be noted that due to the previously described dragging action ofthe leaf spring 201, which causes tight winding of the ribbon, there isno slack to be taken up when the obstruction in the ribbon encountersthe perpendicular arm I18 and places the additional load of the leverI11 on the ribban. The ribbon will thus continue to move and The bellcrank lever I16 will be rocked si-- slfift controlling lever whichconditions the pawl to be shifted by the power operated actuating leverupon the next operation thereof.

Operating came The operation of the ribbon feed bail 286, the

print hammer lever H1, and the transfer bail I82 is effected byoperating cams mounted on the shaft 39 above the gear 4| (Fig. 4). Theoperating cams are assembled in fixed relation with respect to eachother on a sleeve which is mounted on shaft 39 and which has associatedtherewith the driven portion of a spring loaded tooth clutch 2H, thedriving portion of which is keyed or staked to shaft 39. A clutchthrowout lever 2l2 pivotally mounted on shaft H3 is spring biased intoengagement with the driven portion of the clutch 2H and has an arm 2|4(Fig. 2) disposed in the path of a cam projection 2) (Figs. 1 and 6)included on the selector cam barrel 62. With this arrangement, at agiven point in the cycle of operation of the cam barrel 62, camprojection 2H1 rocks the arm 2 which withdraws the clutch throw-outlever 2I2 from restraining engagement with the driven portion of theclutch 2H and permits driving engagement to be established between theshaft 39 and the cams mounted thereon.

The uppermost of the cams is a channel or box cam designated by thereference numeral 2l6, the cam groove 2" (Fig. 9) of which receives thefollower roller 218 rotatably mounted on a bell crank lever 219 rockablymounted on the pivot shaft 22I. The bell crank lever 2I9 is articulatedat 222 to a bar 223 to which it is arranged to impart a reciprocatorymotion due to the fact that the cam groove 2l1 has one ofiset 224 which,when encountered by the follower roll 218, causes the lever 2l9 to rockcounterclockwise upon its mounting shaft HI and in this way the bar 223is reciprocated rearwardly of the typing unit. A lever 226 is alsorockably mounted upon the shaft 221 and is secured at its forward end tothe cam operated bell crank 219 by a clamping bolt 221 which passesthrough a slot 228 in the bell crank 2). The slot 228 providesadjustability in the clamping together of the levers 2l9 and 226. Thelever 226 is effective in the conditioning of functions when they areselected, and its operation will be described later.

The bar 223 carries intermediate its ends an 'eccentrically mountedabutment 230 against which abuts the operating arm 229 of a strikermember or hammer 23| pivotally mounted at 232 (Fig. 1). The bar 223 has2. depending lug 220, and a tension spring 225 has one end connected tothe lug 228 and the other end connected to the operating arm 229 oftriker 23L The striker member 23! is provided at its upper end with amassive head 233 which describes an are as the hammer 23| is rocked andwhich delivers a sharp blow to an impact receiving abutment I38 ofresilient material, such as rubber or leather, carried by the printhammer operating lever arm 1. As indicated in Fig. 9, the oflset 224 inthe groove 2| 1 of cam 216 is very abrupt and very short, so that thereciprocation of bar 223 to its rearmost position is very rapid and thusthe blow imparted by the striker member 23I to the print hammeroperating lever arm H1 is very sharp. The bar 223 has a further functionwhich it performs only under certain circumstances which will bedescribed later.

The cam which is directly beneath the cam 2 I6 is designated by thereference numeral I01 (Fig. 11) and has been described previously as theoperating cam for the transferbail I02. No further description of thiscam is considered necessary.

The final cam in the group is disposed below the cam I81 and isdesignated by the reference numeral 2. This cam, as shown in Fig. 10, iscontoured to impart gradual rotation to a lever 242 pivoted on the stud22l. The lever 242 has a follower roll 243 which rides against the cam24!. As shown in Fig. 10, the radius of the cam 2 increases steadilyfrom minimum to maximum with an abrupt drop between the portions ofmaximum and .minimum radius, and this causes the lever 242 which ispivoted on the shaft 244, to rotate counterclockwise steadily unitl itreaches its extreme counterclockwise position, whereupon it is restoredrapidly to its extreme clockwise position. A bell crank lever whichcomprises a single arm 248 and two arm 249 formance through thecooperation of elements provided therefor.

Spacing mechanism The spacing pawl designated by the reference numeral256 is. articulated to the pin 25I through a spring yield connectioncomprising slot 251, spring 258, and guide pin 259 (Fig. 9). The pivotpin 25| enters the slot 251 and is urged to the forward end of the slotby the compression spring 258. The pin 259 is retained within the slotinside the convolutions of the spring 258 and prevents the spring fromescaping from the slot. The normal movement of the pawl 256 isreciprocatory, due to the rocking of the bell crank lever arm 249 by thecam 2,

but if the movement of the pawl 256 is blocked asit may be under certaincircumstances, the pin 25l may move within the slot and the spring 258will take up the movement imparted by the cam and will restore the pivotpin 25I to the forward end of the slot 251 when the cam follower 243 hasescaped from the highest portion of cam 2. The pawl 256 has at itsopposite end a ratchet engaging prong 26! which engages a ratchet 262 toimpart counterclockwise rotation thereto as the pawl is reciprocated.The pawl is spring biased into contact with the ratchet by a spring 263.The ratchet 262 is fixed to a rotatable carriage spacing shaft 264 whichcarries at its upper end a pinion 266 (Fig. 4) meshing with a rack 261connected to the platen carriage I. A step-by-step movement of thecarriage for letter spacing is effected by counterclockwise rotation ofthe spacing ratchet 262 responding to the reciprocation of the spacingpawl 256. As the carriage is stepped, it rotates the return spring drum'l52 counterclockwise by drawing the belt ll leftwardly, thus tensioningthe spring and storing energy for a carriage return operation. Aretaining pawl 265 (Fig. 9) pivotally mounted at 268 and urged in acounterclockwise direction by a spring 268 engages one after another ofthe teeth of the ratchet 282 and retains the ratchet and thus the platencarriage in the successive positions to which they are advanced by thepawl 256.

Function mechanism The functions of the hereindescribed printingapparatus, such as line feed, shift," unshift, etc., are selected inaccordance with stop positions of the type wheel, as determined bycertain of the stop pins 96 which may be selected by the code discs 9|,are conditioned for operation by the lever 226 actuated by the printhammer operating cam 216, and are performed by the lever arms 248actuated by the spacing canr24i. Any other desired functions may beselected, conditioned, operated in the same manner, and in the presentembodiment of the invention, certain other ones are so controlled, thesefunctions providing for the operation of electrical contacts for circuitcontrol, such as rendering the transmitting mechanism inoperative,remotely controlling apparatus for stopping the operating motor, andoperating an audible signal, such as a bell.

Other functions, particularly those which may conveniently be performedwith great rapidity, may be actuated directly from the print hammeroperating cam 2l6, rather than from the less violent spacing cam 241. Inthe present embodiment of the invention carriage return" and spacesuppression" are so controlled.

Since, as hereinbefore outlined, the selection of functions iscontrolled in accordance with certain stop positions of the type wheel,means must be provided for effecting response of the functionconditioning or performing mechanisms. Such means has been provided onthe type wheel shaft 44 just above the gear 43 and comprises a pluralityof index pins or abutment pins 2" (Figs. 9 and 12) disposed in varioushorizontal planes and in various radial positions with respect to thetype wheel. In certain horizontal planes, only one index pin is found,whereas others contain several pins. The number of pins in a horipivotshaft 216 which will be identified by individual reference numerals inthe description of the several function operations. I

Since the lever 215 and corresponding levers are articulated to thelever 226 (Fig. 9), they undergo movement when the print cam 216operates lever 226, and a lever such as 215 associated with a selectedindex pin 21! moves differently than do those associated with unselectedindex pins. The function levers to which the lever 215 and correspondinglevers are articulated by their disc-like portions 214 are biased totheir unoperated positions by springs 211, and they rotate zontal planeindicates the number of type wheel I stop positions in which aparticular function is selected. Index pins in different horizontalplanes may be disposed in the same vertical plane, indicating that aplurality of functions may be selected simultaneously.

For cooperation with the index pins 21| there are provided a pluralityof superposed levers, the uppermost of which is designated 215 in Figs.9 and 12, pivotally mounted at their forward ends on a pivot pin 218carried at the rearmost end of lever 226 and extending through andsupported in horizontal slots in a plate 213. The levers are alignedwith the index pins 211 in the several horizontal planes. and eachcarries an abutment arm 212 extending leftwardly therefrom at a point onthe lever toward which the associated type wheel shaft index pin 2"points when the shaft is stopped in the position to select the functionrepresented by that pin. At their rearmost ends the lever 215 andcorresponding levers are provided with disc-like portions 214 disposedin notches in the forward ends of associated funcin opposition to thetension of such'springs only when forced to do so. When the lever 226 isactuated by cam 2I6, it carries the pivot pin 218 leftwardly as viewedin Fig. 9, and with it the forward ends of lever 215 and those disposedbelow it. If no index pins 211 are aligned with the abutment arms 212,the lever 215 and corresponding levers pivot about their disc-likeportions 214 and rock idly. If, on the contrary, an index pin is alignedwith an abutment arm 212, it blocks the leftward movement of that arm,and becomes a fulcrum for the particular lever, thus causing the leverto operate as a first class lever to actuate its associated functionlever and rotate the latter counterclockwise.

Certain of the function levers operated by the lever 215 andcorresponding levers are adapted to perform theassociated function andothers are adapted to condition a function. The conditioning is effectedthrough superposed function performing bars, the uppermost of which isdesignated 280, pivotally mounted on the pivot pin 25! carried by thespacing cam operated bell crank lever arms 249. The function bar 288 andcorresponding bars are supported intermediate their ends in spacedhorizontal slots 21.9 in the vertical plate 213 (Fig. 1). They arereciprocated rearwardly when the bell crank lever arms 249 are rotatedcounterclockwise by cam 241 and they may rotate about the pivot pin 25!within the confines of their supporting slots 219. They are biasedcounterclockwise by springs 218.

Fig. 12 displays an exploded perspective view of the functionconditioning and performing levers and also shows the relative angularpositions of the index pins 2" when the lowermost pin is selected. Themechanism for performing the several functions will be described, andreference will be made to/other figures in which parts of the functionperforming mechanisms 'are shown.

Carriage return The uppermost index pin 2" and lever 215 are associatedwith the restoration of the platen carriage I to line beginningposition, which is ac complished by withdrawing the spacing pawl 256 andretaining pawl 261 (Fig.9) from engagement 1 with the feed ratchet 262,whereupon the spring tion levers which are pivotally mounted on theloaded drum I52 acts through the belt I51 to restore the carriage to itsextreme right-hand position. The function lever to which the lever 215is articulated is designated 28!, and this lever is rotatedcounterclockwise when the uppermost index pin 2 is effective upon itsassociated lever 215. The lever 28'! carries upstanding pins 282 and 283located at the left and right of the'spacing pawl 256 and the retainingpawl 265 respectively, and in close proximity thereto. When the lever281 is rotated counterclockwise, it moves the pins 282 and 283 to rightand left respectively and the pins rotate the spacing pawl 256 andretaining pawl 285 clockwise about their pivotal mountings and 288respectively, to withdraw the pawls from engagement with the ratchet282. The carriage, being under no other restraint, responds to the forceexerted by the spring in the drum I52 and moves to its extremeright-hand position, rotating the spacing ratchet 282 clockwise as itdoes so.

It will be noted that the lever 28! is provided, near its rearmost end,with a notch in which are formed shoulders 288 and 281 (Fig. 12) Alatching lever 288 is pivotally mounted at 289 and is biased forclockwise rotation by spring 29! which has one end connected to thelever 288 and the other end connected to the function lever 28!.

When the function lever 28! is in its unoperated or extreme clockwiseposition as viewed in Figs. 9 and 12, the lever 288 is held inengagement with the shoulder 288 by spring 29!. The rocking of thefunction lever 28! counterclockwise to effect a carriage returnoperation permits the lever 288 to escape from the shoulder 288 and tocome to rest against the shoulder 28'! whereby the function lever 28! islatched in its operated position to maintain the pawls 258 and 285 outof engagement with the ratchet 282. The purpose of latching the functionlever 28! in the operated position is to permit the carriage 8!,

298 carried by lever 288. The slotted engagement between lever 288 andlever 292 provides a yielding connection, and a. spring 298, which hasone end connected to the lever 292 and the other end connected to anextension of the lever 288, tends to rotate the lever 292 in acounterclockwise direction which is prevented by a lug 291 carried by afixed plate 295 against which the lever 292 rests. Since the spring 298is disposed between the lug 29'! and the screw 298, the extreme left endof the slot 293 abuts against screw 298. A rod 298 is slidably supportedin the lug 29'! and in a portion 299 of the frame of the mechanism andoccupies the same horizontal plane as the lever 292. The rod 298 slidesfreely within frame memher 299 and the lug 29! and is urged to itsrightward position by the lever 292. The lever I58 which is articulatedto the dashpot plunger rod I58 carries an eccentrically mountedadjustable abutment 38! in alignment with the right-hand end of the rod298. The abutment 38! is similar to the previously described abutment238 and is below the pivotal mounting I5! of the lever I58 so that it ismoved toward the rod 298 as the carriage I8! rotates the lever I58clockwise at the completion of a carriage return operation. When thelever I58 comes to rest in its extreme clockwise position at theconclusion of the carriage return operation, its abutment 38! moves therod 298 leftwardly a distance suflicient to cause it to rotate the lever292 clockwise and position the forward end of that lever in alignmentwith the rod 223 articulated to the bell crank lever 2I9. Lever 292 willoccupy this position as long as the carriage I8! is in its extremeright-hand position and upon the next counterclockwise rocking of thebell crank lever 2I9 by the box cam 2I8, rod 228 will be reciprocatedrearwardly and will communicate its reciprocating motion to lever 282.which will cause the latching lever 288 to be rotated coimterclockwiseout of engagement with the shoulder 28'! and into engagement with theshoulder 288.- The function lever 28! will thus be restored to itsunoperated position and the pawls 258 and 281 will reengage the spacingratchet 282 in preparation for normal spacing operations. The slottedmounting of lever 292 provides a yield connection which may, undercertain circumstances, operate yieldingly on account of a blockingcondition. The carriage I8! may, particularly if it travels through onlya short distance in returning to its extreme right-hand position, reachthat position while the bar 223 (Fig. 9) is being operated by the cam28! and before the bar has been withdrawn to its foremost position.Under this condition the rod 298 might jam the forward end of lever 292against the right-hand face of operating bar 223, whereby the rod 298might be prevented from traveling its normal distance and the carriageI8! be prevented from assuming its extreme right-hand position. Theslotted connection permits the lever 232 to be fully. moved.

by the rod 298, even should the forward end of lever 292 be blocked bybar 223.

Shift and unshijt mechanisms It will be convenient to postpone thedescripfourth level from the top. The, function lever 382 is associatedwith the shift operation by means of which the type wheel is shifted toremove one of the annular sets of type pallets from alignment with theprint hammer I38 and to bring the other set of type pallets intoalignment therewith. The lever 382 does not perform the shift functionbut merely establishes a condition as a result of which the function maybe performed, and to this end it is provided with a projection 383 whichoccupies the same horizontal plane as the bar 288. This bar has itsrearmost end disposed slightly to the left of a latching projection 388of a latching lever 388 which is pivotally mounted on shaft 288 (Fig. 9)and is biased in a clockwise direction by spring 3I8. All leverscorresponding to'lever 388 are biased clockwise by springs 3I8 and arelimited by abutment against stud 388 (Fig. 9). Upon the selection of theindex pin associated with'the lever 385, and upon theoperation of thatlever, the lever 382 is rotated counterclockwise similarly to thepreviously described function lever 28!, and

through its projection 383 it imparts a clockwise rotation to the bar288. The latter bar, in rotating, moves to the right of latchingprojection 388, and at the same time it moves rearwardly due tooperation of bell crank, lever arms 289 by cam 2I8, and becomes latchedin its clockwise position.

The bar 288 carries on the right side thereof a projection 301 which isdisposed in alignment with the lower end of a shifter lever arm 308(Figs. 7 and 8) to which it imparts a counterclockwise motion as viewedin Fig. '7 as the bar 280 is reciprocated rightwardly due to continuedcounterclockwise rocking of the bell crank lever arms 243 by the cam 2.The shifter lever arm 308 is one arm of a bell crank lever pivotallymounted upon the previously described pivot shaft 232 and having itsother arm 3I I extending rearwardly of the printer. The lever arm 3 isbifurcated at its outer end and has disposed in the bifurcation a pin3I2 carried by arm 3I3 of shifter frame 3. The frame 3 is mounted onshaft 232 by means of slot 3I6 so that it may be raised and loweredvertically to lift and lower the type wheel through its horizontal arm3" (Figs. 1 and 4) which is guided on guide screw 3I5 and which engagesthe type wheel hub I23. The operation of the lever am 308 upon theshifter frame 3 is to lift the latter through the articulation of thelever arm 3 to the frame 3 by virtue of the pin 3I2. The frame 3 carriesa pivoted spring loaded detent 3| 8 which has notches at the lower endthereof, either of which may engage a bushing 3I3 on the shaft 232 tomaintain the shifter frame 314 in a position to which it is moved. Aspring 3" (Fig. 1) counterbalances the shifter frame 3 and type wheelIOI, and thus equalizes the forces required to effect shift and unshiftoperations.

Referring again to Fig. 12, it will be observed that a function lever32I similar to the lever 302 and having a projection 322 is pivotallymounted on the shaft 216 below the lever 302 and in articulation withthe lever 325. Two angularly spaced index pins 2'" are disposedin thesame horizontal plane as the levers 32I and 325, which indicates thatthere are two stop positions of the-type wheel shaft which will resultin operation of the function .lever 32I. Lever 32I is associated withthe unshift function of the printer. An operating bar 320 is alignedwith the function lever projection 322 and is also aligned with alatching lever 323 below and similar to the latching lever 306 andprovided with a latching projection 324. The operating bar 320 isarticulated to the pivot pin 25I directly below the operating rod 280and is provided at the side thereof with a projection 326 (Fig. '7)which, when the rod is latched in its extreme clockwise position by theprojection 324 of lever 323, is disposed in operating alignment with alever arm 321 similar to the lever arm 308 but necessarily slightlylonger than that lever arm. The lever arm 32'! constitutes, togetherwith a forwardly extending arm 320, ,a bell crank lever pivotallymounted upon the pivot shaft 232. The outer end of the lever arm 328 isbifurcated similarly to the lever arm 3 and engages a pin 329 carried bya forwardly extending arm 33I of the shifter frame 3I4. When the leverarm 32! is rocked in counterclockwise direction due to movement of theprojection 326 of the operating bar 320, the lever arm 328 will also berocked counterclockwise and will move pin 329 downwardly, wherebyshifter frame 3I4 is moved downwardly to effect an unshift operation. Itis apparent that the lever arms 308 and 321 operate oppositely andsimultaneously so that as one effects movement of the shifter frame, theother is oppositely rotated' and presented in position to be nexteffective in the shifting of the shifter frame 3I4.

It was previously mentioned that the unshifting operation conditioned bythe function lever 32I and performed by the bar 320 may be selected foreither of two stop positions of the type wheel shaft, as indicated bythe presence of two index pins 2' in the same horizontal plane, eitherof which may be effective. One of the plus is associated with theunshift signal and is presented in operating position when the signalcombination assigned to unshifting is received. The other pin ispresented in operative position when that code combination is receivedwhich is assigned to spacing, for the reason that it has been found thatin many instances printing following a blank spacing operation is to beeffected with an unshift condition of the printing mechanism, and it istherefore convenient to effect the unshifting automaticallysimultaneously with the spacing, thus obviating the transmission of aseparate unshift code combination.

Line feed The single index pin immediately below those assigned to theunshift function is associated with the line feed function which is afunction accomplished by rotating the printing platen I39 to advance asheet or web of paper upon which printing is to be effected through adistance sufficient to present a line of blank paper to the printingposition. The selection of the line feed index pin and the rocking ofthe lever 335 (Fig. 12) against the pin causes the operation of afunction lever 332 which is similar to the levers 302 and 32I and whichhas a projection 333 for operating the associated function performingbar 340. A function operating lever 334 is pivotally mounted below thelatch lever 323 on the pivot shaft 268 and is similar to that leverexcept that it has operative connection with the line feeding mechanism,as will be described. and is therefore a .true function performinglever, and it has no latching projection. A separate latching lever 336is provided which is a so pivotally mounted on the pivot shaft 268 and;which has at its right-hand end a forwardly projecting arm 33! whichterminates in an upwardly turned projection 338 which occupies aposition with respect to the lever 334 corresponding to the latchingprojections 304 and 324 of levers 306 and 323 respectively. The lever336 is spring biased in a clockwise direction by spring 333, movement inthat direction being limited by the stud 300 (Fig. 9), and it is capableof counterclockwise rotation independently of the lever 334 to permit itto be cammed in a counterclockwise direction by the operating bar 340and to return to its extreme clockwise position where its latchingprojection .338 latches the operating bar 340 in conditioned position.When the function bar thus latched is reciprocated rearwardly in themanner com.- mon to all of the function performing bars, the lever 334is rotated counterclockwise about the pivot 268. The lever 334hassecured thereto at its right-hand end by screw 3 a link 342 which isprovided with a slot in which is disposed the operating arm 343 of aline feed bail 344. The bail 344 (Figs. 4 and 21) is pivotally mountedin suitable brackets 346 on the rear of the machine and extends slightlyabove the lower end of the previously described line feeding lever I60.The lever I60 travels with the carriage HI and the extent of the bail344 transversely of the machine is slightly greater than the travel ofthe lever I60, so that the lever may be engaged by the bail at anyposition in the travel of the carriage. The line feed lever I60 isprovided with an anti-

